Governing mechanism with variable force



Sept. 8, 1953 Filedbec. 18, 1948,

M. FRENKEL GOVERNING MECHANISM WITH VARIABLE FORCE 4 Sheets-Sheet 1 INVENTOR Sept. 8, 1953 M. FRENKEL 2,651,516

GOVERNING MECHANISM WITH VARIABLE FORCE Filed D60. 18, 1948 4 Sheets-Sheet 2 INVENTOR Sept. 8, 1953 FRENKEL 2,651,516

GOVERNING MECHANISM WITH VARIABLE FORCE Filed Dec. 18, 1948 4 Sheets-Sheet 3 Flair 2,1 123 31 FIG 5 INVENTOR.

Sept. 8, 1953 Filed Dec. 18, 1948 i M. FRENKEL GOVERNING MECHANISM WITH VARIABLE FORCE 4 Sheets-Sheet. 4

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INVENTOR Patented Sept. 8, 1953 GOVERNING MECHANISM WITH VARIABLE FORCE Meyer Frenkel, London, England Application December 18, 1948, Serial No. 66,126 In Great Britain December 24, 1947 5 Claims. 1

This invention relates to centrifugal governing mechanisms for prime movers and other machines.

g It is an object of this invention to provide constructions of centrifugal governing mechanisms, which can be adjusted, also during running of the governor, and with maintenance of desired degrees of sensitivity and stability of the governing action, to provide forces of different magnitudes to operate the control organ of an engine or engines to be governed, in other words, constructions of governors, which can be adjusted during running of an engine to govern this engine in different states, which may require different governing efforts, or which can be adjusted to govern different engines requiring different governing efforts.

It is a further object of this invention to provide constructions of centrifugal governing mechanisms, which can be adjusted, also during running of the governor, to provide forces of different magnitudes to operate the control organ of an engineor engines to be governed, and which can be set, also during running of the governor to govern to any desired speed of rotation of the shaft of an engine or engines to be governed.

It is a further object, to provide constructions of governor, in which adjustment of governing force takes place automatically.

It is known that in an ordinary centrifugal governor, before sleeve-motion and thus governing can taken place, the change in the centrifugal force on the rotating bodies due to a change in governor spindle speed must produce a force on the governor sleeve which is suflicient to overcome the resistance of the engine control mechaniSm v for direct acting governors (or the resistance of the servomotor control for servo-motor types) as well. as the frictional resistance (F) of the sleeve itself.

Thus a governor, to be sensitive, must be so designed that for the desired change in governor spindle speed Aw at which governing is to take place, the change in centrifugal force AC0 corresponding to this change of spindle speed only (no change of radius of the path of the rotating bodies as yet takes place) is of magnitude where ,3 is the ratio in which, depending on the construction of the governor, an axial force on the governor sleeve is translated into a force on the rotating bodies in the line of action of the centrifugal force on them. In other words, a change in centrifugal force on the rotating bodies as function of a change in radius of their path, which would increase the total change of centrifugal force and would support the required motion of the governor sleeve, cannot arise before the change of centrifugal force as function of the change of spindle speed only has produced motion of the governor sleeve against the resistances.

In Equation 1, with Mb the mass of bodies rotating at radius R i. e. it is seen that the change in centrifugal force arising due to a change of spindle speed only is directly proportional to the original spindle speed. I

When now an ordinary governor is designed to be sensitive at a high spindle speed, w1-when =0(w1)=2M Rw a co 7 is large this means that for a required change in spindle speed, 'at which governing is to take place, condition.(1) is satisfied,

i. e. the change in centrifugal force on the rotating bodies as function of the given change in spindle speed only is sufficient to overcome the control organ resistance and the sleeve friction thus causing governing action.

If one now attempts to use the same governor at a small spindle speed, wz (having made the necessary spring etc. adjustments), when is proportionally smaller, and the Awz at which governing is to start, will also be smaller than the change in spindle speed Awi for the high speed governor if governing within the same percentage limits is desired, it is seen that (2)' 2= b 2' -2 the change in centrifugal force on the rotating bodies as function of the change of spindle speed,

is very much smaller than for the high speed governor (more than the proportion of the spindie speeds), while the resistances of the control mechanism and the sleeve friction have remained the same, so that condition (1) cannot be fulfilled.

Thus, at the small spindle speed, the change in centrifugal force on the rotating bodies due to a required change in spindle speed only will not be able to overcome the control organ resistance and sleeve friction, so that the governor cannot work at the low spindle speed.

Conversely, when a governor, which is sensitive at low spindle speeds, is used at. high spindle speeds, it will, due to the ACa the changes of centrifugal force as function of the changes of spindle speed, being correspondingly .largenxbe" sensitive even to the normalcyclic variationsof spindle speed occurring at constantmeanspindle speed, and will be useless in this way.

To achieve the objects of the invention in'view of the above properties of conventional governors. this invention provides:

-A governing .mechanism' with a centrifugal speed responsive devicecomprising a spindle, a set of centrifugal bodies, .a guiding-means for retating said centrifugal bodies with the/rotary speed of said spindle and for. permitting. radial motion of said centrifugalbod-ies relative to said spindle, a sleeve member-axially movable relative to said spindle-rand a connecting-means between said centrifugal-bodies and-said sleeve member for relating'radialmotion of said centrifugal bodies. and axialmotion of said sleeve member, said governing mechanism further comprising a separate control sleeve axiallymovable relative to said spindle, a means. for connecting said control sleeve to an engine to be governed, a resilient balancing means, a connection between said resilient balancing means and said control sleeve, and a secondary spring means situated betweenand connecting said sleeve member of said speed responsive device and said control sleeve for permittingaxial motion of: said. sleeve member of said speed responsive device independently of said control sleeve.

.. Further this invention provides:

In and for a governing mechanism, a centrifugal speed responsive device =comprising a spindle, a set of centrifugal bodies, a guiding means for rotating said centrifugal bodies about said spindle andfor. permitting radial motionof said centrifugal bodies relative to said spindle, asleeve member axially movable relative to said spindle, a connecting -means between said centrifugal bodies and said sleeve member for relating radial motion of said centrifugal bodies and axial motion of said sleeve member, and manually operable means fcr varying the centrifugal mass effective in said speed responsive device. independently of the axial position of said: sleeve member, said means comprising a frame situated adjacent at least one centrifugal body," a mounting for-rotating said frame with said spindle, means mounted in said frame for locking at least said one centrifugal body in a radial position nearest said spindle in which connection of said centrifugal body with said sleeve member is disestablished, and for releasing said centrifugal body from said radial position, and manually operable means for actuating said locking and releasing means indepcndently of the axial position of said sleeve member.

. .As. described in somedetail with reference to thedrawing, the provision-of a separate controlsleeve (i. e. the sleeve which actuates the control .organ of the engine beinggoverned) which is separated from the sleeve member by a secondary spring means and is also acted upon by the resilient balancing mechanism for the speed responsive device, effects that a change of shaft speed which would in a conventional governor be insufficient to overcome the control sleeve resistance, already moves the sleeve-member.

Thereby the action of the centrifugal force is reinforced as-a function of the changeof radius of the centrifugal bodies which takes place with sleeve-motion while the control sleeve is yet stationary,.and further-due to the action of the secondary spring means between the sleeve-member and the control sleeve, so that altogether the control sleeve .is set in motion by a change of shaft speed which is smaller than that required to overcome the same control-sleeve resistance by means of a conventional governor. This increases sensitivity, particularly at the lower end of a range of speeds in a variable speed governor, and has valuable-efiects on theoperationof the governor.

Ehefollowing canbe said with reference to the provision for variable eifective mass of the centrifugal bodies.

It-will :be seen that the condition of making M, the effective mass of" the centrifugal bodies variableas function of the speed setting can be fulfilled :if the total range of'set speeds to be covered is divided into m part ranges, and the effectiveumass. of thecentrifugal. bodies is made to vary in steps from range .to range, remaining the same within each part range of set speeds.

It can be shown that, with the same resilient balancing mechanism andrno other alterations being effected. inthe: governor, the characteristic curve (Cl-curve -of centrifugal force for equilibrium at the beginning of .the steady stateplotted against corresponding-radii of vthe centrifugal bodies) is the same for all'such part ranges.

Accordingly; if the governor is stablein one of the part ranges it will be stable in. all part ranges of speed-setting.

The inventicnwill now be described by way of example and :in detail with reference to the accompanying drawing,- inwhich:

Figs. 1" and 2 are respectively a sectional elevation and section plan of a detail illustrating :the provision for. adjusting the effective centrif- :ugal 'mass of". a governor;

Fig. 3 is a sectionalelevation of a governor embodying the separate control sleeve with secondary spring means, as Well as the provision for adjusting theeifective centrifugal mass of the governor;

Figs. land 5 are respectively a sectional elevation and sectional plan of a further detail illustrating alternative provision for adjusting the effective centrifugal mass of a governor, Fig.-. 5 being a section on line 5-5 of Fig. 4;

Fig. 6 is a sectional elevation of a detail illustrating the provision of a separate control-sleeve with secondary spring means;

Fig? is .a sectional elevation illustrating an alternativepro'vision :for adjusting the effective centrifugal mass of a governor.

. In the'detail-of Figs. 1 and 2, 12 balls, denoted by reference numerals 21, form the centrifugal bodies of the speed responsive device, which are rotated about the governor spindle .22 in the radial slots 24 of a guiding cage 23, which is "keyed to the governor spindle. The balls 2| and cage 23 are interposed between two conical cups 25 and 26 respectively, mounted respectively on ball bearings 21 and 28, to be able to rotate freely due to their contact with the balls 2|. The ball bearing 21 is mounted with its other ring on collar 29, which is'keyed to and rotates with the spindle '22, so that conical cup member 25 is incapable of axial motion relative to the governor spindle.

on the governor housing 52, which engages either of two wires 33 stretched on sleeve member parallel to the governor spindle axis. For one direction of rotation roller 32 engages one wire '33 and for the opposite direction the other wire The device for varying the effective mass of the centrifugal bodies comprises radial rods 31,

-mounted in the cage-rim 38 at each radial slot 24 of the cage 23, so as to be cap-able of radial motion between two positions, in the outer of which the ball 2| is left free to move radially in its slot 24, while in the inner position the cup-shaped ends 39 of rods 31 lock the ball 2| against the inner rim 40 of the slot 24, so that the ball then has no contact with the conical cups in any of their positions, and cannot move at all under centrifugal force.

In this example, 12 balls are provided, and the variation of the effective centrifugal masses is indicated to take place in four stagesthree of the balls, symmetrically disposed about the governor spindle 22, are always left in action to produce governing in the highest range of spindle speeds,

' so that no locking rods 31 need be provided in the slots 24 of these 3 bal1s-and the further balls are brought into action by withdrawing three of the locking rods at a time, as the spindle speed to be governed is reduced, until finally, at the lowest speed-range to be covered, all 12 balls are in action. The bringing into action, or taking out of action, of groups of balls, may be synchronised with suitable alterations of the effect of the balancing spring means, to provide for smooth action of the governor over its whole range of speeds.

The adjustment of locking-rods 31 is shown in this example to be effected by means of angled levers 4|, mounted on pins 42 fixed on the respective radial extensions 34 of the collar 29, which rotates with the governor spindle. .The levers 4| engage the ends 43 of the rods 31, which are slotted to allow for obliquity, with their'one ends, and at their other ends the levers 4| carry pins 44, which engage the slots 45 in the radial extensions of the sleeve 41, which is mounted on the governor spindle to rotate therewith and to be capable of axial motion relative to this spindle. Each locking rod 31 has a radial extension of sleeve 41 corresponding to it, and the slots 45 in these radial extensions 46 are so shaped, that, through one axial motion of the sleeve, a desired three of the levers 4| perform their motion, thus locking or unlocking a set of three balls, While, during the same motion of the sleeve 41, the other levers 4| remain in the positions they occupied before. For a following motion of sleeve 41, a further three levers 4| move, the others remaining in their previouspositions, so that by motion up or down the governor spindle of sleeve "the 6 desired adjustment *of the effective centrifugal masses takes place stage by stage during running of the governor.

The fulcra 42 of levers 4| are mounted in slides '48, which are movable in the radial direction against springs 49, which prevent the mechanism from being rigid, and further effects that, in the locked position, the rods 31 always exert a force due to the spring 49 on the balls, so that the balls are firmly locked and cannot move about.

The axially slidable sleeve 41, which rotates with the governor spindle, carries a ring 35 mounted on a ball bearing 50 at its end. Ring 35 engages a double lever 5| with two radially oppositely placed pins 54, this'lever being fixed to axle 36 mounted in the governor housing 52,

by means of which adjustment of the effective centrifugal mass of the governor takes place from outside the governor housing during running of the governor.

It will be understood from the example given, that the locking or release of the balls or groups of balls can be effected by many kinds of mechanism besides that described without departing from the inventione. g. the locking device on the cage may be worked from inside a hollow governor spindle, or from mechanisms disposed about the governor spindle, and connected to the cage through a central opening in one or both of the conical cupswhich kind of arrangement would eifect an appreciable saving in overall diameter of the assembly. Further, some such arrangement connecting to the cage from the inside would enable cup 25 of this example to be mounted through bearin 21 on a non-rotating part of the governor, so that it will then move under the same conditions as the cup 26, which'is mounted on the non-rotating sleeve 30.

Further, the locking of the balls need not be effected necessarily by a locking rod movable in the radial direction but could also be effected by levers mounted on the cage, or other suitable means.

Figs; 3 and 4 show an embodiment of the invention with a provision for adjusting the effective centrifugal mass on a larger scale than possible with the provision illustrated in Figs. 1

and 2; together with the provision of the separate control-sleeve and secondary spring-means between this and'th'esleeve-member of the speed responsive device.

The provisionfor increasing the force exerted on the control-sleeve56 dueto the action of the balls 2| comprises the sleeve-member 30 which is "separate from the control sleeve 56 instead of being in one piece with it as in other constructions;

and the secondary spring 55 connecting the sleeve-member 35 with the control-sleeve 56.

Thecontrol-sleeve 56 is from its other side acted upon by the balancing spring-means |09|D6- -|03-||l1||l5||l2| |2|0|, as described in the following, and actuates the control-mechanism of the engine to be governed through the lever-mechanism 515B.

It will be seen that, for example, for an increase in spindle speed, the sleeve member 30 can move axially downwards due to the increase in centrifugal force acting on the balls by only overcoming the' frictional resistance to axial motion of this sleeve, which is very small, and the force of the spring 55, but without having to overcome the resistance, which in an ordinary construction is the main resistance against motion of the sleeve, namelythat of the control organ of the engine' to be governed; This enables the balls to ascompared to; the 2ba1ls f. epr viou ly d s ri ed emb dim nt: ar d in tw es n. t

same lplanejoi which the inner race. has 9 balls 7 and the outer race has 18 balls. 'I he cups here .haye two conical, portions 1 eaeh-.the cup 25: has thedditionalcon ca par -9 he en ra rix o which isparallelto that-of conical surface 25, and cone 26 has the additional conical surface 92, opposite conesurfa-cetZ. .Correspondingly,

1cage'23 has two rows of slots, row 24 and rw-33 at the two different mean radii of the races. The

centre line-ofevery secondslot 03 andof every slot 24 arerarranged tobe on the same radius, so that amokns devi m is n a od- 37 m ed in the rim 38 of the cage, with an extension (to, the inner ring of slots 24, serves both these bgllsat. the same time. -The balls in the outer row @ofslotswhich have no counterpart in the inner -row, are servedbylocking devices comprisin rod .31 only, exactly asin the example described with ier ce to Fi s. 1 nal T e o e le as-=w s w o m ha is of th l e i gdericeare de otedby th same renc numerals a hcse sedf r th previous y described embodim nt-and the. a t o at his m c ani wil be understood by reference to thisprecedingdescription.

n thi examcle: fr m a nit alth ee balls.

which are ect ve. at a hi h s indl s eed 0 .even twobal1s), the effective nllmberef balls; can

be stepped up, with falling spindle speed toa tetal oi' 7-ba ls wi a' e ed H herofbalIs' ea h. st p In th s embodiment, the .--b ancins s rin mea s h s a rov s on f r va n u ing ru ning o t esovem he at k o t b la cin PI'iIlEfiIQQH ac i g o h c n rol ee e v5 th ra e. of hissp i g means being-theori ng o force taking place for unit motion of one end :of the spr n -means .re1ative t he othe alo th -g v rn spind eax s)- :fincomer-i onstruct onauy a curve ab tment-surfa I extend ng ro he on rol sl 55 uided t m ve alon t e gov rnor sp nd aasainstwhich sur ac 0 Iv b t roun d head o 4 mm r cally a ran d e ca e n s 3, thes .sp in s b ngmount d mpai s o a x eex endin n rmally-to the ov rn r s i e. t

either side of this spindle. The casings surroundingsaid Springs I03 each comprise two parts, I05 and I06, each of which is connected to one end of the spring I03, and havinga mounting of two small'ball races in a cage I01 between them, which permitsthe two parts of the casing to move relative to one another only along the axis of the spring. According y, the enclosed spring I03 is only subjected toiorces acting along its axis, and not to bending moments, which are taken up by its casing.

The spring casings are arranged in pairs, the

casings of each pair .being arranged symmetrically to the governor. spindle axis, i.e., enclosing the sameangle. a. with this axis. The mounting spindle axis.

crzthcse cas nssona l 1 1 is-suchr at th an ab tw n t e a is of he a -and he common s n x s can b i s d d ng mnning of-thegovernor from outside the gov? ernor casing, i.e. two of the casings, which are substantially parallel, are mounted on the axle llM'il filf; while the other two casings, whiohare also substantially parallel, are mounted on a sleeve filwrrounding the axle I04, both the axle Mandthe sleeve-82 being angularly adjustable from outside the, casing of the governor. The compression of each spring I03 can also be varied, by mean of the screw threaded rods I08 rotation'of which moves plate I09 in slot III) of the part I06 of the cas ing of the spring. The part of the casing denoted by I05, whichis ad,- rjacent theabutment surface I0 I, is provided with a-roller I12 to facilitate motion of part I05 relative to; the abutment surface. .The angle t between the normal to the abutment surface at the point of contact of roller H2 and the governor spindle axis depends in thiscontruction onthe shape of the-abutment surface, in the example oi a cylindrical abutment surface theangle \ZIFIZ.

In operation of the governor the control. sleeve membero c la u ndr a pr n 10 in their; casings, which each have, a rate It for motion of their ends relative to one another a one the -o axis, sh and ne he i-providing a combined spring effect for the motion of thegovernor sleeve along; the governor spindle-of a rate It motion may be able to take place.

Figs... stand 5 show an alternative detail of-- a governor embodying provision for adjusting the efiective centrifugal mass.

in contrast to the previously described example, two sets of balls are here arranged on two idifierent planes disposed along the governor spindle axis, between two similar sets ofconical cups in different positions along the governor Conical cups, occupying corresponding positions in the two sets, are connected by tube 123, and are mounted by bearing I on sleeve part of the speed responsive device and by bearing 124 on an axial extension of sleeve 30, so :that these cups can rotate relative to sleeve -:30 under the influence of the balls 2I,- and can -move the sleeve along axially along the spindle 22 as well. The other two corresponding conical cups "I26 and I2! are mounted through bearings I29 and I30 on two plates 29 and I3I, of which the plate25 forms an extension of member which is mounted on the governor spindle and fixed by means of a key to rotate with the spindle, and the plate ISi is fixed to member 41 'by'rocls I32 at positions all round the circumference. The cage 23 for the upper set of balls iskeyed to the spindle 22, whereas the cage I33 for the lower set of balls is mounted on rotating plate I30, so that it also rotates with spindle speed. The arrangement is made further rigid .by-the rods I32 connecting, besides the extension from rnember, 2 9 and plate I 30, also the rim 38 of ase 23 a he r m 4 o case 1 3 The locking devices "compriseradial rods 31, as in the first embodiment described, mounted in the rims 38 and'l34 of cages 23 and I33 respectively. In this case the mechanism shown acts for both sets of ballsat once, and in order to achieve'this, the angledlever II acts on a connecting piece I35 between the rods 31 in corresponding positions in the two sets, engaging connection I35 by means of a pin I36 at slot I31 in a position midway between the two sets'of balls, in order to ensure substantially equal forces on both these levers 31 for the two sets. To make the mechanism elastic, and to provide a spring loading on a rod 31, which has looked a ball, so that this ball cannot move about, the rod 31 for the'lower set of balls is guided in boss I38 of the connection I35, and the spring I33 between the boss I38 and the flange I40 on this rod 31 pushes the latter inwards.

In the example shown here, the effective number of balls may be increased by suitable steps from an initial three (or even 2 or 1 ball) at the higher mean spindle speeds to be governed to a total of 18 balls for the lowest part range of spindle speeds to be governed;

It will be understood that in all the speedresponsive devices described the provision for'varying the effective mass of the centrifugal bodies by means of locking rods 31 may be in the nature of a spring loaded switch, e. g. a compression spring may be provided betweenthe rim 38 of the cage and the cup 39 of the locking rod.

Alternatively, a tension spring may be'provided between the rim 38 of the cage at its outside, and the slotted end 43 of rod 31.

Other ways of spring-loading the locking provision are also possible without departing from the spirit of this invention.

Fig. 6 illustrates as a detail the provision of the separate control-sleeve 56 actuating the control-organ of an engine to be governed through lever 51, which is separated from the sleevemember 30 of the speed responsive device by the secondary spring means 55, like numerals'denoting like parts as on Fig.3. The resilient balancing mechanism is here represented as the direct acting spring 84, abutting on casing 85, for the sake of clarity. j

In operation, for an increase in spindle speed and corresponding increase in centrifugal force, for example, the-sleeve member" 30 can move downwards merely against the frictional resistance to axial motion of this sleeve, which is negligibly small. Such axial motion takes place there fore without having to overcome the main resist ance against sleeve-motion in conventional governors, viz. that of the control organ of the engine to be governed. This enables the balls to move radially outwards without "any motion of control-sleeve 56 as yet taking place, thus increasing the centrifugal force-acting also as function of the increase in ball-path radius, and further compressing the secondary spring means 55. F r

This'continues until the excess force exerted on the control-sleeve 56 by the secondary spring 55, over that exerted by balancing spring 84 'is suflicient to overcome the control-organ resistance, and the control-sleeveifi begins to move downwards too, in consequence of a change of shaft-speed which in a conventional governor would have been much too small to produce any motion of the sleeve against an equal control organ resistance. Thus thecontrols are adjusted and spring 84 compressed.

Meanwhile the sleeve-member 30, having gone through zero axial velocity, will reverse its direction of motion, and sleeve 33 and the control sleeve 56 will move in opposite directions for a short timedue to inertia of the control-sleeve and connected component--until stopped by friction. vlIf the adjustment of the control organ is then not the required one, the control-sleeve will be set in motion again by a further oscillation of the type described, until a new steady state is reached, through an oscillatory process of the control-sleeve which is much less than that of the sleeve 30, and-less than that of the combined sleeve of a conventional governor.

The main point of the construction .is' that through the action described, the axialforce on the control-sleeve which is caused by a change in centrifugal force AC as function of a change of spindle speed onlywhere AC is'itself too small to move the control sleeveis brought to a value considerably greater than ACRE), which is sufiicient to move the control sleeve. 7

Thus, due to constructions according to this invention, in variable speed governors a far wider range of speeds will be opened up, particularly at the lower end of the speed range at which in a conventional governor the change of centrif ugal force due to a given change in shaft speed would not be sufficient to move the sleeve at all.

On the other hand, through such a construction, it is possible to exert a considerably greater force on a control-mechanism than it would otherwise be possible without a servomotor.

Fig. '1 shows a detail of a governing mechanism, where instead of a ball and cup type speed responsive device a hinged weight type is provided with means for varying the effective mass of the centrifugal bodies. The centrifugal bodies 2M, of cylindrical shape, are rotated about the governor spindle 22 on arms 2fl2-hinged at pin 203 on sleeve 204,- which sleeve rotates with the governor spindle but cannot move axially-thereto.

The sleevemember 205 is connected to the centrifugal bodies by means of arms 206, which are hinged at pins 201 on the weights 20I. The hinged arms 206 have ends 208, with a slot 208 therein extending ata certain calculated angle to the axis of the arm 206, engaging respective pins 209 on extensions '2I0'on the sleeve 205.

A locking device as described with reference to Fig. 1, comprising a rim 38 mounted on the spindle 22 so as to rotate therewith (detail not here shown), and radial'locking rods 31 mounted in said rim, with flat ends 39 for contacting the weight together with all the other levers, sleeves and the like for actuating the locking rods, in combination with the slotted connecting arms 206, form' the device for disengaging a weight from connection with the sleeve member, and for re-engaging such a weight to connection with the sleeve member.

. -In Fig. '1, a weight 20I is shown inv the locked position in which it is also-disengaged from connection with the sleeve, which moves and fulfills its functions only under the influence of the weight on the left hand side, and of other weights, which are not shown. For the locked weight, on the right hand side, it will be observed, that the slot 208 in the arm 206 is so designed, that in the locked position of the weight 20I the slot 208 extends parallel to the spindle axis, so that pin 209 on the sleeve can slide up and down the slot 208 without hindrance- The weight shown free on-the left hand side: exerts a pulLdueto centrifugal force on the sleeve; through its engagement with pin 209 nae-{tension Zlllbi the sleeve, which is resisted by balancing spring 2 H, the Sleeve thus being stationary or carrying "out its motions under the influence of the centrifugal force and of the balancing spring. A required number of weights may, of course be provided on such a speed responsive device, and due to the locking provisions already described with reference to the preceding examples, any number of these weights can be successively locked or unlocked, so as to provide a wide range of governing eiiorts to be provided by the sleeve, or a wide range of spindle speeds to be governed to, or a wide range of these variations combined.

I claim: 1. In and for a governing mechanism, a centrifu'g'al speed responsive device comprising 'a spindle, a set of centrifugal bodies, a guiding means for rotating said centrifugal bodies about said spindle and for permitting radial motion of said centrifugal bodies relative to said spindle, a sleevemember axially movable relative to said spindle, a connecting means between said centi'ifugal bodies and said sleeve nie inber for'iclati'ng radial motion of said centrifugal bodies and axial motion of said sleeve member, and manually operable means for varying the centrifugal mass effective in said speed responsive device indepeha uy of the axial position of said sleeve member, said means comprising: a frame situated adjacent at least the centrifugal body, a inountiilg for rotating said frame with said spin die, rneans'mounted in said frame for locking at least said on centii fu gal body ina radial po. sition nearest said spindle, inwhichconnection with said sleeve member is disestablished, and for releasing said centrifugal body from said radial position, and manually operable means for actuatingsaid locking and releasing means independently of the axial position of said sleeve em e V 2. In and for a governing-mechanism, a centrifugal speed responsive device comprising a spindle, a set of balls, a slotted guiding page mounted on said spindle for rotating said balls about said spindle and for permitting radial inotion of said balls, a first membenwhich is axially immovable rel ative to said spindle and a second member which is axially movable relative to said spindle, both said membersbeing freely rotatable relativeto said spindle, atleastsaid second mem ll ing a cup-shaped co ta t isu iac vfor said balls, the said balls being interposed between oppositely fa cing contact surfaces of said-two members, asleeve member axially movable relative to said spindle, a bearing formountingsaid second axially movable androtatable member on said sleeve-member, and manually operable means for varying the centrifugal massefiective in said speed responsive device independently of the axial position of said sleeve-member, said means comprising aframe situated adjacent at least one of said balls, a mounting for rotating said frame with said spindle, means-mounted in said frame for looking at least said one ball in the innermost position in said slotted "guiding cage in which contact of said ball with said; axially movable second member is disestablished, and for releasing said ball from said position, and manually operable mcans'for'actuating said lockingand releasing meansindependently of the axial position of said sleeve-member.- I

3; An engine governing mechanism with a cell"- trifugal speed responsive device comprising a spindle, a set of balls, a slotted guiding cage fiiced on said spina -em rat-sung said balls about said spindle and for perinimg radial motion of said balls, at nfstmember which is 'a'xially immovable" relative to said spindle, a second m mber white is axially'movable relative it said spindle, both said 'inembersbeing freely 'rotatfable relative to said spindle, at least one of "said members having a cup-shaped contact surface for said balls sai'd balls being interposed between oppositely facing surfaces of said two members, a sleeve member axially movable 'i ela tive to said Spindle and abearin'g" for jmo iintihg said second, axially movable and rotatable'ineiiiber' on said sleeve member, the saidenginegoverning mechanism further comprising asep'arate control sleeve axially movable relative to said spindle, a means forc'onnecting said "con"- trol sleeve to an engine to be go emea, a resilient balancing means, a connection between said resilient balancing means and said control sleeve, and a secondary spring means situated between and connecting said sleeve-member of said speed responsive device and said'cont'rol sleeve, for permitting axial motion of said sleeve member of said speed'rs'ponsive device independently of said control sleeve.

4. An engine governing mechanism 'asclaiined in claim 3, in which said resilient balancing means is situated on the side 'of said'control sieeve which is remote from said sleevemeinb'ei or said speed responsive device, and in which said secondary spring means is 'arianged 'sy'rn metrically about said spindle and b'etvieenfsaid sleeve member of said speed responsive device 2 and said control sleeve.

5. In and for a'govefn'm g' mechanism, 'a'cnti'ifugal speed responsive device as claimed claim 2, comprising't'wo of said sets "of balls arranged in two planes normal to said spindle and displalbed r'elative to one another aion'gsaid spindle, one of said slotted guiding aagesror eac of said sets or balls and said "first i-otatablean'd axial 1 y rnbvlble member and said seiion'dlii'lit'l;able and axially movable member for each or" said sets dreams a rigid connection for said were; tatable and axially movable second 'fil inbels, Said s1ee've member axially movable rehiilve'to said spindle, said bearing for mounfifig-saiase'cefia members on said sna e member, and Saia'man- 'uauy operable means ib'rvaiyifig' the number :of balls efiectlve "as centliffigal mass'e'seah set o f b alls indebe n dentiy b'f the asaai posiuonb'f said sleeve member.

aefefefiee's Cited in die file-of this-"patent UNITED STATES enema 

